WO2004034923A1 - Douche buccale et buse de pulverisation pour la production d'un jet de liquide et systeme de nettoyage de dents - Google Patents

Douche buccale et buse de pulverisation pour la production d'un jet de liquide et systeme de nettoyage de dents Download PDF

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Publication number
WO2004034923A1
WO2004034923A1 PCT/EP2003/011431 EP0311431W WO2004034923A1 WO 2004034923 A1 WO2004034923 A1 WO 2004034923A1 EP 0311431 W EP0311431 W EP 0311431W WO 2004034923 A1 WO2004034923 A1 WO 2004034923A1
Authority
WO
WIPO (PCT)
Prior art keywords
spray nozzle
oral irrigator
nozzle
pump
piston
Prior art date
Application number
PCT/EP2003/011431
Other languages
German (de)
English (en)
Inventor
Oswald Gromer
Andreas Kramp
Michael Sauer
Michael Stolper
Norbert Schaefer
Karl Herzog
Original Assignee
Braun Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10248336A external-priority patent/DE10248336A1/de
Priority claimed from DE10248338A external-priority patent/DE10248338A1/de
Priority claimed from DE10248339A external-priority patent/DE10248339A1/de
Application filed by Braun Gmbh filed Critical Braun Gmbh
Priority to AU2003285294A priority Critical patent/AU2003285294A1/en
Priority to AT03778276T priority patent/ATE464019T1/de
Priority to US10/531,484 priority patent/US8052627B2/en
Priority to EP03778276A priority patent/EP1555954B1/fr
Priority to DE50312628T priority patent/DE50312628D1/de
Publication of WO2004034923A1 publication Critical patent/WO2004034923A1/fr
Priority to US13/250,447 priority patent/US20120021371A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • F04B49/126—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
    • A61C1/00—Dental machines for boring or cutting ; General features of dental machines or apparatus, e.g. hand-piece design
    • A61C1/0061—Air and water supply systems; Valves specially adapted therefor
    • A61C1/0084—Supply units, e.g. reservoir arrangements, specially adapted pumps
    • A61C1/0092—Pumps specially adapted therefor
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
    • A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
    • A61C17/02—Rinsing or air-blowing devices, e.g. using fluid jets or comprising liquid medication
    • A61C17/0202—Hand-pieces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B05B1/3431—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves
    • B05B1/3436—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves the interface being a plane perpendicular to the outlet axis

Definitions

  • the invention relates to an oral irrigator, a spray nozzle and a tooth cleaning system according to the preamble of the independent claims.
  • Spray nozzle in the context of this application can also be understood to mean a nozzle for dispensing a water jet which does not consist of individual drops.
  • spray nozzle in the context of this application can also be understood to mean a nozzle for dispensing a water jet which does not consist of individual drops.
  • EP 0 841 038 A1 it is known to arrange in the spray nozzle a paddle wheel which rotates about its axis of rotation and which is set in rotation by the cleaning liquid supplied to the paddle wheel.
  • the cleaning liquid reaches the outlet via a channel in the paddle wheel arranged at an angle to the axis of rotation.
  • the cleaning liquid leaves the outlet of the spray nozzle in the form of a rotating liquid jet.
  • a tooth cleaning device similar to an oral irrigator is known from DE 199 59 188 A1.
  • a cleaning scraper designed as a spoon-like additional part is required.
  • a pressure of 3 to 6 bar and an outlet speed of 5 m / s to 15 m / s are provided for the liquid. It is described that higher values should be avoided because the liquid jet is then perceived as unpleasant. These values are supposed to be a good compromise between high cleaning efficiency and a pleasant impact intensity his.
  • the disadvantage is that the scraper cannot get into all interdental spaces or in other tooth areas.
  • the present invention is therefore based on the object of providing an oral irrigator and a spray nozzle for the oral irrigator with improved cleaning action.
  • the liquid jet should be able to remove firmly adhering plaque in the proximal area and on the gum line.
  • the spray nozzle for generating such a liquid jet should work as wear-free as possible and be of simple construction.
  • a device for the spray nozzle is to be created, which enables extensive cleaning of the teeth and gums.
  • the cleaning liquid is fed to a spray nozzle at high pressure, a liquid jet emerging from a nozzle outlet having a high speed and consisting of microfine drops.
  • a thin, fast-moving liquid film is formed by the nozzle outlet, which then changes into microfine drops at high speed.
  • the cleaning effect is improved compared to the prior art.
  • a high pressure of at least 15 bar is sufficient to enable the microfine droplets to form reliably, the velocity of the liquid jet preferably being higher than 25 m / s.
  • the velocity of the liquid jet preferably being higher than 25 m / s.
  • a significantly better cleaning effect is achieved at a pressure of over 20 bar and / or a speed of over 35 m / s.
  • the solution according to the invention makes it possible to dispense with the use of a scraper or another additional part.
  • the microfine drop size is perceived as relatively pleasant.
  • the irrigator can be operated simultaneously in connection with a brush part or another additional part that directly touches the teeth.
  • the additional part can be designed as a brush ring arranged concentrically around the nozzle outlet. Due to the high impact energy of the drops on the plaque layer, the cleaning liquid is pushed away to the side. The shear forces generated tear the plaque surface open, forming pits and craters. Since the liquid jet consists of a large number of drops, this process is repeated in quick succession. In this way, the plaque layer is removed in layers.
  • the cleaning liquid is fed to the spray nozzle at high pressure.
  • the pressure is above approximately 15 bar, in particular between approximately 25 bar and 55 bar, the best cleaning results being able to be achieved in a pressure range from 35 bar to 45 bar.
  • the cleaning liquid must be atomized or sprayed.
  • Particularly small drops can be generated with the same nozzle diameters and pressures if the liquid jet is designed as a diverging hollow cone jet.
  • the diverging hollow cone jet also has the advantage that the spray area is enlarged with increasing distance from the nozzle outlet, which enables faster cleaning.
  • the generation of a full cone or flat jet is also conceivable.
  • the formation of the jet is decisive for the formation of the microfine drops.
  • These can be generated in that the cleaning liquid is formed in the nozzle outlet as a thin film which is evenly distributed on the inner wall of the nozzle outlet. When leaving the nozzle outlet, this evenly distributed film tears into the microfine drops just behind the nozzle outlet.
  • Adhesive plaque layers can be removed particularly well with a liquid jet consisting of drops, the drops of which have a size of approximately 5 ⁇ m to 10 ⁇ m and a speed of at least 23 m / s, preferably approximately 45 m / s to 55 m / s.
  • a spray nozzle for generating a liquid jet for an oral irrigator with a nozzle body which has a chamber into which a liquid can nal to the supply of pressurized cleaning liquid opens and from which a nozzle outlet for the exit of a cleaning liquid jet emanates, that the chamber is connected to a vortex chamber of approximately round cross-section for generating a circulating stream of cleaning liquid, from which the nozzle outlet, which preferably emanates from one, extends centrally there is a cylindrical constriction and an optionally subsequent, in particular approximately conical, extension. If necessary, the extension can also be omitted or not be conical.
  • This design makes it possible to generate a liquid jet consisting of microfine drops of high speed, which is able to remove plaque due to the drop speed.
  • a cleaning carried out with the spray nozzle designed as a hollow cone nozzle enables a gentler cleaning with the same service life due to a significantly lower abrasion of the epithelial cell layer than with an electric toothbrush.
  • the spray nozzle enables an additional reduction of approximately 60% plaque, especially in the approximal area.
  • the spray nozzle does not require any moving parts that would be subject to increased wear.
  • a constriction in the form of a bore with a diameter of approximately 0.1 mm to 0.2 mm and a depth of approximately 0.05 mm to 0.2 mm has proven to be advantageous for producing the microfine drops at high speed.
  • a constriction designed in this way ensures that the cleaning liquid emerging from the swirl chamber enters the optionally subsequent expansion at high pressure and high speed.
  • an expansion in particular in the form of a cone or hollow cone, has proven to be advantageous, the expansion following the constriction.
  • cleaning fluid is applied to the wall of the hollow cone as a uniformly distributed thin film, which film rotates around the axis of symmetry of the extension due to the vortex chamber. Due to the high tangential speed, the film tears into the microfine drops as soon as it leaves the hollow cone, especially just behind the nozzle outlet.
  • a cone or hollow cone with a length of approximately 0.2 mm to 0.5 mm and an opening angle of approximately 20 ° to 70 ° has been found to optimize the formation of the drops.
  • This nozzle geometry is also characterized by the fact that even with high droplet velocities small volume flows, for example less than 80 ml / min, are possible without the nozzle geometry becoming so small that the costs for production increase. In this way, extremely small nozzle geometries, which also have a shorter service life, are avoided.
  • the nozzle which is designed as a hollow cone, also has the advantage that it has a very stable spray pattern even in the case of manufacturing inaccuracies or contamination.
  • the outlet can be constructed in a compact and thus space-saving manner if it is formed in a nozzle attachment arranged on the nozzle body.
  • a further simplification in the manufacture of the nozzle attachment is if the constriction and the expansion are in a separate component, e.g. a nozzle plate are arranged.
  • the assembly of the nozzle plate in the nozzle attachment is only associated with a small additional effort, while the production is more economical in terms of accuracy, dimensional accuracy and costs with a nozzle plate.
  • the nozzle plate can be made of a different, more wear-resistant material.
  • the nozzle attachment ensures interchangeability when it is connected to the nozzle body by means of a detachable connection.
  • the detachable connection can be designed either as a screw connection or as a latching and plug connection. This allows the nozzle attachment to be replaced, for example, in the event of damage.
  • a nozzle body designed in this way enables conventional nozzle attachments to be accommodated, which are operated with a substantially larger volume flow at a considerably lower pressure.
  • the arrangement of a pressure piece in the spray nozzle has proven to be advantageous for the design of the swirl chamber.
  • the pressure piece is arranged in a chamber which is formed between the nozzle attachment and the nozzle body.
  • the part of the pressure piece located in the nozzle body or nozzle attachment is inserted with a press fit or fixed by means of locking elements arranged on the nozzle attachment or nozzle body. This fixation facilitates the assembly on the one hand and on the other hand the pressure piece is captively connected to one of the two parts when the nozzle attachment is changed.
  • the pressure piece can have a pot-shaped part at both ends.
  • the first cup-shaped part faces the constriction in the nozzle attachment and forms the swirl chamber with its interior.
  • the second cup-shaped part is oriented towards the liquid channel in the nozzle body.
  • At least one opening is arranged in the first cup-shaped part, through which the cleaning liquid can get into the chamber from the interior of the first cup-shaped part. A free drainage of the cleaning liquid is ensured if the interior of the cup-shaped part is connected to the chamber via at least one opening, but preferably three to four openings.
  • the openings are designed as axial slots through the cup-shaped part, the regions of the cup-shaped part lying between the slots form spring arms which support the fixing of the pressure piece.
  • the function of the spring arms is supported if the pressure piece is made of an elastic material, e.g. a plastic.
  • the arrangement of the swirl chamber in the pressure piece as a separate component ensures particularly simple manufacture.
  • the swirl chamber is formed by the interior in the first cup-shaped part which is placed on the area around the constriction, the constriction being the outlet from the swirl chamber.
  • the cup-shaped part lies around the narrow point.
  • a particularly good sealing effect is achieved when the cup-shaped part lies flat. This type of sealing prevents deformation in the pressure piece. Such deformations could occur with a linear seal if the cup-shaped part seals with an edge.
  • sealing surfaces it would also be conceivable to design the sealing surfaces as a cone.
  • the cone angle of the nozzle plate and pressure piece must match exactly.
  • two flat surfaces are cheaper to manufacture.
  • locking hooks can also be provided in the area around the constriction, which cooperate with locking points on the outer circumference of the pressure piece.
  • This Fixation also has the advantage that when changing the spray nozzle, the pressure piece is held captively in the nozzle attachment.
  • Access to the swirl chamber is formed by at least one opening in the first cup-shaped part which is perpendicular or at an angle of less than 90 ° to the axis of symmetry of the pressure piece. It has been shown that the beam formation is influenced by the number, the cross section and the position of the openings. Good results have been achieved with two opposite openings designed as slots.
  • the openings open into the vortex chamber approximately transversely and with a center offset to the longitudinal axis of the vortex chamber.
  • the size of the center offset and the angle at which the openings open into the swirl chamber are also decisive for the formation of the beam.
  • a center offset which is so large that the liquid jet emerging from the openings strikes the opposite wall of the swirl chamber at an angle of less than 45 °, has been found to be favorable. In this angular range, the beam can most effectively transfer its energy to the vortex that is being formed.
  • the cleaning liquid is supplied to the openings via grooves in the first cup-shaped part which run parallel to the axis of symmetry of the pressure piece.
  • This type of feed avoids radial feed, which in turn would take up a large amount of space.
  • the spray nozzle can thus be designed with a small diameter.
  • a pressure piece with two cup-shaped parts is advantageous if the liquid channel lies on an axis with the constriction.
  • a spray nozzle with a smaller axial extent can be achieved if the liquid channel is oriented approximately radially to the constriction.
  • the area facing the liquid channel can be omitted, which simplifies the construction of the pressure piece.
  • a spray nozzle according to one of the device claims is preferably arranged on the handpiece. If the spray nozzle can be exchanged for another nozzle on the handpiece of the device, the device can be operated in different operating modes.
  • the interchangeability allows, for example, the use of a conventional jet and / or spray nozzle.
  • the spray nozzle according to the invention is operated at a high pressure with a small volume flow and a normal oral irrigator nozzle with a large volume flow at a low pressure. If both nozzles are operated with approximately the same hydraulic power, the pump can be driven by an electric motor, the pump being switchable, for example by means of a switchable transmission.
  • Switching between the operating modes can take place without additional effort or devices in the handpiece if the nozzle attachment is used for the detection of the operating mode to be set.
  • a certain pressure builds up in the device.
  • a pressure sensor can be arranged between the pump and the spray nozzle for detecting the pressure of the cleaning liquid conveyed to the spray nozzle, wherein a signal corresponding to the detected pressure of a control unit can be fed from the pressure sensor and the electric motor can be controlled by the control unit with the operating mode assigned to the detected pressure.
  • the high-pressure mode with the spray nozzle according to the invention produces a high torque and a low speed.
  • a speed or torque sensor can be arranged on the pump or on the electric motor for detecting the speed or the torque of a rotor of the pump or the electric motor, with a signal from a control unit corresponding to the detected speed or the detected torque from the speed or torque sensor can be supplied and controlled by the control unit of the electric motor and / or the pump and / or the transmission with the operating mode assigned to the detected speed or torque. It is understood that the torque and / or the speed can also be carried out by measuring the current drawn by the motor. In summary, it should be noted that switching between the operating modes can be carried out by pressure or current detection.
  • an eccentric shaft or a crank pin in its overall eccentric dimension is adjustably arranged on a drive element, a crank mechanism being provided for a pump of the oral irrigator and the oral irrigator with a drive element which can be driven by a drive device about an axis of rotation and a drive element parallel to an eccentric overall dimension arranged to the axis of rotation on the drive element, serving as an output eccentric shaft or crank pin.
  • the output on the crank pin has at least two movements. These movements enable the plunger of a pump to be operated with at least two different strokes. In this way, the pump delivers a small volume flow with a small stroke, while the pump delivers a large volume flow with a large stroke.
  • the adjustment is made by reversing the direction of rotation of the drive.
  • the adjustment of the eccentricity is characterized by a Reversal of the direction of rotation on the drive shaft by a particularly low mechanical effort, whereby the installation space of the eccentric drive is not significantly increased. No additional locking of the set total eccentric dimension is necessary, since the eccentricity depends solely on the direction of rotation.
  • This type of adjustment has the further advantage that the adjustment under load, e.g. the pump. An additional adjustment unit or external intervention to change the eccentricity is not required.
  • the eccentric drive is also characterized by low wear, since the components are only moved to one another when switching between the eccentricities, the switching usually taking place in the unloaded state.
  • the setting of the eccentricity as a function of the direction of rotation of the drive shaft is particularly simple if the output element has a disk that is pivotally mounted on the drive element about the pivot axis, if the disk carries a crank pin that is parallel to the pivot axis with a second eccentricity extends and if the drive element has an axially protruding driver which is pivotable with the drive element and projects between two stops defining the two end positions, the stops being arranged on the disk.
  • the slave contacts the respective stop.
  • the direction of rotation of the disc relative to the drive element causes the overall eccentric dimension of the crank pin to be enlarged or reduced compared to the drive element.
  • the eccentricities of the disk and the crank pin can also be varied within wide limits, the eccentricity of the disk should be smaller than that of the crank pin. This ensures that the disc is always in contact with the driver.
  • a largest and a smallest overall eccentric dimension of the crank pin relative to the axis of rotation of the drive element can be realized with a crank mechanism if the stops are arranged in such a way that the eccentricities of the disk and the crank pin add up or subtract.
  • the angular distance between the stops on the disc is 180 °. The change in the angular position of one or both distances, depending on the changed stop, leads to a reduction or increase in one or both overall eccentric dimensions.
  • the stops can be formed in the disc in the form of at least one circular arc-shaped, concentric groove in which the driver can be moved.
  • the ends of the groove then form the stops for the driver in the respective direction of rotation.
  • the groove preferably extends over an angular range of up to 180 ° and can penetrate the pane completely or be formed only to a certain depth of the pane.
  • Two or more such symmetrically arranged grooves can also be formed in the disk, in each of which a driver is arranged movably and thus a symmetrical support load occurs.
  • stops are arranged as areas of the disk with a larger radius.
  • a particularly good guidance of the disc is achieved by the arrangement of two symmetrically arranged drivers, which interact with stops which are likewise arranged symmetrically on the disc. With the symmetrical attack, tilting of the disc due to a tilting moment is effectively avoided. The bending and torques as well as the transverse forces from the lifting-side load on the crank pin are supported by the stops and / or the disk.
  • the drivers can be produced particularly simply and therefore inexpensively if they are integrally formed on the drive element as pins.
  • the drivers can also be arranged on the drive element as separate components, in the form of bolts. This version has the advantage that the drivers are interchangeable.
  • either the stops or the drivers are adjustable.
  • the adjustability can be torque-dependent, for example.
  • the stops are provided with a spring against which the drivers rest. According to the size of the torque generated by the drive device, the stops are displaced by the drivers along the spring travel, which results in a change in the eccentricity. In this way, it is possible to fine-tune or individually adjust the stroke of the pump piston generated as a function of the direction of rotation and thus the volume flows and pressures in conjunction with adapted throttles of the liquid conveyed. As a result of the torque dependency, the stroke can be set by regulating the drive device.
  • the tongue is a tongue which is arranged at the respective end of the groove or on the driver.
  • the adjustability can be varied according to the spring characteristic of the spring used.
  • Coil springs which allow a large spring travel, have proven to be favorable for the adjustability within relatively wide limits. For large torques or small spring travel, disc, leg or leaf springs are advantageous.
  • the disk For the rotatable mounting of the disk, it is mounted on the drive element with a bolt designed as a separate component.
  • the assembly of the bolt can, however, be omitted if it is molded onto either the disk or the drive element.
  • the drive element For receiving the disk, the drive element is disk-shaped at one end. The disk is mounted in this disk-shaped area. This configuration is particularly favorable if the drive element is injection molded from plastic.
  • the formation of the disk-shaped area as a separate component enables the creation of switchable eccentric drives which can be adapted to different requirements with regard to volume flow and, if appropriate, pressure of the liquid to be conveyed.
  • the corresponding disk-shaped area is to be installed, the disk-shaped areas differing only in the eccentricity of the mounting of the disk and the correspondingly arranged drivers.
  • the disk-shaped area can be provided with a plurality of receptacles for the disk and correspondingly arranged receptacles for the drivers, the receptacles of the disk having different eccentricities to the drive element.
  • the eccentric drive or crank drive can be adapted to the respective requirements with a disk-shaped area and the correspondingly selected bearing point for the disk, thereby reducing the number of parts.
  • the drive element can be driven by a drive device via a gear transmission.
  • a gear wheel is attached to the drive element.
  • the arrangement of the gear on the drive element is structurally simple if the gear is integrally connected to the drive element, preferably by means of injection molding of plastic, or forms the drive element.
  • the use of plastic leads to a reduction in the weight of the eccentric drive.
  • the crank mechanism has a compact design that can be varied depending on the requirements.
  • the crank mechanism is disc-shaped, while in the cylindrical design it is radially small. With the use of disc or cylindrical components, simple and therefore inexpensive to manufacture elements are used.
  • crank pin which is part of an eccentrically and rotatably mounted to the drive element crankshaft and of a driver arranged on the drive element, which limits the rotation of the crankshaft to the drive element.
  • the eccentricity of the crank pin on the crankshaft is superimposed on the eccentricity that results from the arrangement of the crankshaft in relation to the drive element.
  • the eccentricities due to the arrangement of the crankshaft to the drive element and the design of the crankpin on the crankshaft can be varied within wide limits, the eccentricity of the crankshaft to the drive element preferably being smaller than that of the crankpin. This ensures that the crank arm always lies against the driver.
  • the eccentricities arising as a result of the direction of rotation are determined by the arrangement of the driver on the drive element.
  • the driver is a radially extending web that engages the crank arm of the crankshaft.
  • the arrangement of the driver is particularly simple if it is molded onto the drive element.
  • a largest and smallest overall eccentric dimension of the crank pin to the drive element can be achieved if the crank arm is carried along by the driver in a position pointing radially outwards and a position pointing radially inwards.
  • the two positions and the bearing point of the crankshaft are in line.
  • the driver is also arranged almost radially.
  • a piston of a pump of the oral irrigator is axially displaceably guided at two bearing points of the pump housing, which are arranged at a distance from one another.
  • a further reduction in the loads in the bearing points is achieved if at least one of the bearing points is arranged in an end region of the displacement path of the piston in the pump housing. This enables torque reduction for this bearing point almost to zero, so that the loads are limited to a force attack. There is particularly little effort if the pump chamber is designed as a bearing point. It is also conceivable to implement the bearing point on the piston end of a link guide.
  • the pump housing is expanded in such a way that the cover surfaces of the link guide are preferably received by the housing. 23 is designed so that it completely receives the cover surfaces of the link guide as the piston end, the bearing point having an axial extent which is greater than the stroke of the piston. This ensures that the cover surfaces of the link guide are always in the area of the bearing point.
  • a large bearing point, which receives the cover surfaces of the link guide, is avoided if the link guide is not arranged at the end of the piston, but according to FIG. 24 between the two ends of the piston. In this way, a bearing point that is significantly smaller in diameter can be made possible. Depending on the intended use, the unfavorable bearing forces that may occur are negligible.
  • crank pin can be rotatably mounted in a sliding block, which is movably arranged in a sliding block guide connected to the piston, transversely to the direction of movement of the piston.
  • crank pin in a sliding block with a bore ensures, on the one hand, a relatively firm and large-area connection of the moving crank pin to another component. In this way, the high surface pressure of the crank pin is compared to another component. Despite the still high relative movement between the link guide and the sliding block, the surface pressure towards the piston is considerably reduced due to the very large area compared to a crank pin, which has a positive effect on the service life of the components in question. In addition, the loads on other components, in particular those on the bearing points of the piston and the seal, are also reduced.
  • the motor power can be reduced, which reduces the current consumption of the pump, or a smaller motor can be used.
  • the reduced load also allows the crank pin to be designed with a smaller diameter, which also contributes to reducing the friction.
  • the flat support enables greater power transmission, so that a pump designed in this way can be designed for higher pressures.
  • a reduction in the load is further achieved in that the sliding block and the sliding guide consist of a pair of materials with low friction.
  • a further reduction in the surface pressures is achieved in that the piston is gimbally connected to the crank pin.
  • a gimbal or gimbal-like arrangement is structurally particularly easy to achieve if the sliding block has a cylindrical cross section and the sliding block guide is designed as a bore with a corresponding cross section in a piston-fixed part and the sliding block is thus rotatably arranged about its longitudinal axis.
  • This mobility allows the movement to be balanced around an axis.
  • Another important advantage of the cylindrical sliding block is that the entire lateral surface of the sliding block is in contact with the sliding block guide. This configuration is characterized by an extremely low surface pressure. The components have a long service life due to the low specific loads.
  • the piston is also rotatable about its longitudinal axis.
  • the link guide is thus able to perform a compensating movement about a second axis. The interaction of the movements movement of the sliding block and the sliding block guide around two axes, which is necessary for tolerance compensation of a crank pin arranged obliquely.
  • crank pin and the link guide Additional friction between the crank pin and the link guide is avoided if an elongated hole for passage of the crank pin is formed in the wall of the link guide, which slot has a greater width than the diameter of the crank pin.
  • an elongated hole designed in this way undesirable friction is avoided, in particular in the case of a crank pin arranged obliquely in space.
  • crank pin helps to further reduce the friction between the crank pin and the sliding block if the crank pin is rotatably mounted in the sliding block in a bearing which is inserted into a hole in the sliding block.
  • the bearing is preferably designed as a plain bearing.
  • the friction can be further reduced by a suitable choice of material.
  • plastics are particularly advantageous when the requirements are not too high. Plastics have good sliding and emergency running properties and are characterized by good lubrication.
  • the eccentric drive or crank drive can have a drive shaft and the eccentricity of the crank pin relative to the drive shaft of the eccentric drive can be adjustable. This configuration enables the crank pin to be switched to a different eccentricity, with which a different piston stroke can be realized. This enables the pump to be operated in two operating modes.
  • the pump inlet and / or the pump outlet can be arranged axially to the longitudinal extent of the pump chamber.
  • the pump inlet and / or the pump outlet may be arranged radially to the pump chamber, it being possible for them to be arranged radially next to one another.
  • Pump inlet and pump outlet can also be arranged axially one behind the other.
  • the piston or the wall of the pump chamber has a longitudinal groove or flat, through which at least one of the connections is connected to the pump chamber, this ensures a connection of the connections to the pump chamber, which is independent of the position of the piston.
  • the seal can be arranged radially enclosing the piston between the bearing points of the piston. This decoupling of the bearing point and the seal greatly reduces the direct entry of wear particles. This leads to a considerable reduction in wear on the seal. This reduced wear leads to an extended service life of the seal without there being any pressure reduction in the pump chamber.
  • the seal is exposed to particularly low loads if it is arranged centrally between the bearing points.
  • the seal is only slightly radially loaded by tilting moments.
  • a further reduction in the entry of wear particles from the bearing points is achieved if the piston has a larger or smaller diameter in the area between the bearing points than in the area of the bearing points.
  • the seal is fixedly arranged in the pump housing and has a sealing lip, which is in radial contact with the piston in a sealing manner.
  • the piston can be dimensioned with a smaller diameter due to the omission of the circumferential groove. This enables a reduction in the required installation space and the oscillating masses.
  • FIG. 1 shows a section through a first embodiment of a spray nozzle
  • FIG. 2 an enlarged representation of the nozzle plate according to FIG. 1
  • FIG. 3 a perspective illustration of the pressure piece according to FIG. 1
  • FIG. 4 a top view of the swirl chamber according to FIG. 1,
  • FIG. 5 shows a section through a second embodiment of a spray nozzle
  • FIG. 6 shows a section through a third embodiment of a spray nozzle
  • Figure 7 a device with a spray nozzle.
  • Figure. 8 a section through a first embodiment of an eccentric drive or
  • FIG. 9 a section of the eccentric drive according to FIG. 8 in the plane II-II,
  • Figure 10 the eccentric drive according to Figure 8 in the changed direction of rotation, in the plane
  • FIG. 11 a section of the eccentric drive according to FIG. 10 in the plane III-III,
  • FIG. 12 a perspective illustration of the eccentric drive similar to FIG. 8 with two drivers
  • FIG. 13 a spur gear and a disk of the eccentric drive
  • FIG. 14 a crank mechanism with variable stops
  • FIG. 15 shows a section through a second embodiment of a crank drive or eccentric drive in the plane VIII-VIII of FIG. 16,
  • FIG. 16 a section of the eccentric drive according to FIG. 15 in the plane IX-IX,
  • FIG. 17 a section through the eccentric drive according to FIG. 15 in the changed direction of rotation in the plane X-X of FIG. 18,
  • FIG. 18 a section of the eccentric drive according to FIG. 17 in the plane Xl-Xl
  • FIG. 19 a perspective illustration of a first exemplary embodiment of a plunger pump
  • FIG. 20 a sectional illustration of the plunger pump according to FIG. 19,
  • FIG. 21 a section of the plunger pump according to FIG. 19 in the area of the eccentric drive
  • FIG. 22 shows a section of a second exemplary embodiment of a plunger pump in the region of the pump chamber, the arrangement of the piston and crank being interchanged with respect to FIG. 19,
  • Figure 23 shows a schematic partial representation of an embodiment of the arrangement of a possible bearing point
  • FIG. 24 shows a further exemplary embodiment of the arrangement of a possible bearing point in a schematic partial representation
  • FIG. 25 a further illustration of a spray nozzle
  • FIG. 26 shows zones of a tooth
  • FIG. 27 an illustration of a drop striking plaque
  • FIG. 28 a representation according to FIG. 28, but at a later point in time
  • FIG. 29 a representation according to FIG. 28, but after the plaque has been removed
  • FIG. 31 is a perspective view of another embodiment of a spray nozzle
  • Fig. 34 a front view of the brush element.
  • the spray nozzle 1 shown in FIG. 1 consists of a nozzle body 2 which is connected to a nozzle attachment 3 by means of a screw connection 4.
  • a liquid channel 5 for the cleaning liquid is arranged in the nozzle body 2.
  • the nozzle body 2 forms, together with the nozzle attachment 3, a chamber 6, into which the liquid channel 5 opens. A pressure piece 7 is inserted in this chamber 6.
  • the pressure piece 7 is radially expanded cup-shaped at its two ends. With the first cup-shaped part 8, the pressure piece 7 sits on a nozzle plate 9. The second cup-shaped part 10 surrounds the area in which the liquid channel 5 opens into the chamber 6.
  • the second cup-shaped part 10 has four evenly distributed axial slots 11 through which the cleaning liquid supplied in the liquid channel 5 can flow into the chamber 6.
  • the first cup-shaped part 8 has two grooves 12 formed axially on the circumference of the pressure piece 7. In the region of the grooves 12, the cup-shaped part 8 is surrounded by a ring 13. This polyamide ring 13 seals the circumference of the cup-shaped part 8, so that the grooves 12 act as channels. At the lower end of the grooves 12 there are radially extending channels 14 formed as slots, which extend approximately tangentially into a swirl chamber 15.
  • the swirl chamber 15 is formed by the interior of the first cup-shaped part 8 and the nozzle plate 9. At the same time, the nozzle plate 9 closes an opening 16 in the nozzle attachment 3.
  • the nozzle plate 9 in turn has a passage 17 through which the cleaning liquid emerges from the swirl chamber 15.
  • the passage 17 of the nozzle plate 9 is shown enlarged.
  • the passage consists of a bore 18 which forms the outlet from the swirl chamber 15.
  • the bore 18 has a diameter of, for example, 0.15 mm and a length of, for example, 0.1 1 mm.
  • a diverging hollow cone 19 connects to the bore 18.
  • the hollow cone 19 has an opening angle of, for example, 30 ° and a length of, for example, 0.35 mm.
  • the cleaning liquid set in rotation in the swirl chamber 15 by the approximately tangential channels 14 is accelerated in a swirling manner due to the small diameter of the bore 18.
  • the cleaning liquid then enters the hollow cone 19.
  • the cleaning liquid forms as a uniformly distributed thin film on the wall of the hollow cone 19 due to the vortex movement and the decompression.
  • the film rotates around axis A at high speed.
  • the film tears into a large number of drops with an average size of approximately 10 ⁇ m, which move at a speed of approximately 50 m / s.
  • the drops in their entirety form a hollow cone.
  • the pressure piece 7 in Figure 3 shows the two cup-shaped parts 8, 10.
  • the second cup-shaped part 10 is divided into four areas by four slots 11 evenly distributed around the circumference. Due to their shape, these areas act as spring arms 21.
  • the spring arms 21 are supported on the nozzle body 2, so that the first cup-shaped part 8 with the surface 22 is pressed against the nozzle plate 9.
  • the two grooves 12 are arranged on the circumference of the first cup-shaped part 8.
  • a channel 14 is connected to each of the grooves 12, approximately tangentially, which opens directly into the swirl chamber 15. The cleaning liquid flows from the chamber 6 to the swirl chamber 15 via the grooves 12 and the channels 14.
  • the position of the channels 14 relative to the swirl chamber 15 can be seen in FIG. 4.
  • the channels 14 do not lead radially from the grooves 12 to the center, but run in opposite directions parallel to one another and enter the vortex chamber 15 with a center offset X.
  • the center offset is selected so that a jet entering the swirl chamber 15 undisturbed strikes the wall of the swirl chamber at an angle of less than 45 ° and is diverted into a circulating flow on the wall.
  • FIGS. 5 and 6 show a second embodiment of the spray nozzle 1.
  • the nozzle body 2 is not arranged radially but preferably approximately tangentially on the nozzle attachment 3 with respect to the axis of symmetry of the nozzle attachment 3.
  • the liquid speed channel 5 also laterally into the chamber 6.
  • the chamber 6 is closed with a cover 23.
  • the pressure piece 7 is simplified in that no second cup-shaped part is necessary.
  • the swirl chamber 15 is in turn arranged in the first cup-shaped part 8.
  • the pressure piece 7 is supported on the cover 23 so that the surface 22 rests sealingly on the nozzle attachment 3.
  • the sealing effect of the surface 22 is supported by a spring 24 which presses the pressure piece 7 against the nozzle attachment 3.
  • the cleaning liquid in turn reaches the swirl chamber 15 via grooves 12 and slots 14, which are arranged similarly as in FIGS. 1 to 4.
  • the spray nozzles 1 in FIGS. The bore 18 and the hollow cone 19 are arranged in the nozzle attachment 3.
  • the projections 25 have an axial extent of approximately 3 mm.
  • the projections 25 serve to set an optimal working distance by placing the spray nozzle 1 with the projections 25 on the areas to be cleaned.
  • the device 26 in FIG. 7 comprises a liquid container 27 which can be filled with cleaning liquid by the user.
  • the cleaning liquid is conveyed from this liquid container 27 by means of a pump 28, which is driven by an electric motor 29, via a hose 30 to a handpiece 31.
  • the spray nozzle 1 is interchangeably arranged on the handpiece 31.
  • a sensor 32 is arranged on the electric motor 29, which measures the torque generated by the electric motor 29 and then supplies a signal to the pump 28 so that it can be operated in the operating mode which corresponds to the spray nozzle used.
  • the pump 28 If the spray nozzle 1 according to the invention is used, the pump 28 generates a volume flow of 50 ml / min at approximately 40 bar in the high pressure mode. This corresponds approximately to a mechanical or hydraulic output of approximately 2000 ml / min bar or approximately 3.3 W. If a conventional spray nozzle is arranged on the handpiece 31, the sensor 32 recognizes the torque which has changed compared to the spray nozzle 1 according to the invention and the pump 28 is operated in the oral irrigator mode. The pump 28 delivers a volume flow of approximately 300 ml / min with a pressure of 6 bar. This results in a mechanical or hydraulic output of approximately 1800 ml / min bar or 3.0 W. Due to the approximately the same Mechanical power in both operating modes, the device 26 can be operated with a pump 28 and an electric motor 29.
  • the eccentric drive described below has at least two different movements on the output.
  • the different movements on the output can be adjusted with minimal effort.
  • the adjustment is also possible without external intervention in the drive.
  • the space available for the eccentric drive is not significantly larger.
  • the eccentric drive 101 in FIG. 8 has a drive element 102, which is designed as a drive shaft and is mounted in two bearing points 103, 104.
  • a spur gear 105 is attached to one end of the drive shaft.
  • the spur gear 105 is connected to a drive device, not shown, and is used to drive the drive shaft.
  • a disk-shaped area 116 for receiving a disk 106 is integrated in the spur gear 105.
  • the spur gear 105 has a bore 107 arranged with an eccentricity e1.
  • the disc 106 is rotatably supported in the bore 107.
  • the disk 106 has a bore 109 arranged with an eccentricity e2, in which a crank pin 110 serving as an output is inserted.
  • a connecting rod 111, which drives the piston, not shown, of a pump acts on the crank pin 110.
  • the disk 106 has a groove 112 into which a driver 113 designed as a bolt engages, which is fastened in the spur gear 105.
  • the disk 106 and the crank pin 110 are arranged such that the eccentricities of the disk e1 and the crank pin e2 are aligned in a line. In this position, the eccentricities e1 and e2 add up to the largest total eccentric dimension e3.
  • the crank pin 110 transmits to the connecting rod 111 a stroke which corresponds to twice the total eccentric dimension e3.
  • FIG. 9 shows the spur gear 105 with the disk 106 arranged eccentrically thereon and the crank pin 110 arranged eccentrically to the disk 106.
  • the driver 113 attached to the spur gear 105 engages in the circular-shaped groove 112 of the disk 106.
  • the groove 112 extends over 180 °.
  • the ends 114, 115 form the stops for the driver 113.
  • the largest overall eccentric dimension e3 arises when the spur gear 105 is driven in the direction of rotation shown.
  • the driver 113 runs in the groove 112 of the disk 106 up to the stop 114. If the driver 113 abuts the stop 114, it rotates the disk 106 and thus the crank pin 110 with the spur gear 105 in the direction of rotation shown.
  • FIGS. 10 and 11 show a changed position of the crank mechanism 101 according to FIGS. 8 and 9, the spur gear 105 being driven in the opposite direction of rotation.
  • the drive shaft At its end facing the disk 106, the drive shaft has a disk-shaped region 116 which is designed to receive the disk 106.
  • the spur gear 105 is arranged on the circumference of the disk-shaped region 116.
  • the connecting rod 111 When switching in the direction of rotation shown, the connecting rod 111 opposes a braking torque, so that the crank pin 110 and thus the disk 106 remain in their position.
  • the driver 13 arranged in the spur gear 5 now runs from the stop 114 in the groove 112 to the stop 115, so that the spur gear 105 rotates by 180 ° relative to the disk 106.
  • the disk 106 is taken along by the driver 113.
  • the spur gear 105 and the disk 106 rotate again at the same speed.
  • the eccentricity e2 of the crank pin 110 counteracts the eccentricity e1 of the disk 106.
  • the smallest total eccentric dimension is set.
  • the crank pin 1 10 now only transmits to the connecting rod 111 a stroke that corresponds to twice the smallest overall eccentric dimension e4.
  • the crank mechanism 101 in FIG. 12 shows an eccentric drive 101 which is slightly modified compared to FIG. 8, the toothed ring of the spur gear 105 being shown as a chain line.
  • the spur gear 105 has two symmetrically arranged drivers 113 which run in two concentrically arranged circular arc-shaped grooves 112 in the disk 106. The ends of the grooves 114, 115 form the stops for the drivers 113.
  • the eccentric drive 101 shown in FIG. 106 has a spur gear 105, the ring gear of which is shown as a chain line.
  • the spur gear 105 has a plurality of bores 117, 117 ', 117 ". These bores 117, 117', 117" serve to receive the disk 106, the bores 117, 117 ', 117 "having different eccentricities e1, e1', e1" ,
  • the spur gear 105 can thus be used for various requirements by mounting the disk 106 in the corresponding bore 117, 117 ', 117 ". corresponding bores 118, 118 ', 118 "are assigned to gene 117, 117', 117", in which the driver 113 is arranged.
  • the disk 106 in turn has stops 114 ', 115' which, however, are not arranged in the disk 106 as grooves 112, but as regions 119 with a larger radius on the circumference of the disk 106.
  • the disk 106 according to FIG. 14 has two concentrically arranged grooves 112, in which two drivers 113 run.
  • a coil spring 120 is arranged such that, depending on the direction of rotation of the drive shaft, each driver 113 bears against a coil spring 120 and the disk 106 rotates at the speed of the drive shaft.
  • the coil springs 120 have the effect that the drivers 113 do not lie completely against the end of the respective groove 112.
  • the crank pin 110 is no longer in line with the center of the disk 106 and the drive shaft, and the eccentricity e1 only adds up in part to the eccentricity e1 of the disk 106.
  • the resulting largest overall eccentric dimension e3 is thus smaller. Shocks are also dampened when the direction of rotation is switched.
  • the coil springs 120 are designed with respect to their spring characteristic so that even slight changes in the torque generated by the drive device are sufficient to change the spring travel via the driver 113 transmitting the torque. With changes in the spring travel, the disk 106 rotates toward the drive shaft, which leads to slight changes in the position of the crank pin 110 and thus in the overall eccentric dimension e3, e4. In this way, the total eccentric dimension e3, e4 and thus the stroke of the connecting rod can be fine-tuned by a torque control on the drive device or the drive shaft.
  • the spur gear 105 and the drive shaft are formed in one piece as a drive element 102.
  • the drive shaft is rotatably supported in the bearings 103, 104.
  • the drive shaft has a bore 121 in which a crankshaft 122 is mounted.
  • the crankshaft 122 is arranged in the drive shaft with an eccentricity e1.
  • the crank pin 110 which is connected to the crankshaft 122 via a crank web 123, has an eccentricity e2 with respect to the crankshaft 122.
  • the connecting rod 1 1 1 is attached to the crank pin 110.
  • the crankshaft 122 is arranged such that the crank pin 110 is oriented radially outward with respect to the bearing point of the crankshaft 122. In this position, the eccentricities e1, e2 of the crankshaft 122 and the crank pin 110 add up to the largest overall eccentric dimension e3.
  • the crank pin 110 transmits to the connecting rod 11 1 a stroke which corresponds to twice the total eccentric dimension e3.
  • the drive element 102 is driven by the drive device (not shown) via the spur gear 105 in the direction of rotation shown.
  • a driver 113 formed on the drive element 102 is arranged such that it drives the crankshaft 122 in the position shown in FIG.
  • FIGS. 110 and 111 show the arrangement of the eccentric drive 101 according to FIGS. 15 and 16, the spur gear 105 being driven in the opposite direction of rotation.
  • the crankshaft 122 rotatably arranged in the drive shaft rotates by 180 °.
  • the crank pin 110 is arranged radially inward with respect to the mounting of the crankshaft 122, so that its eccentricity e2 is now aligned against the eccentricity e1 of the crankshaft 122.
  • the smallest total eccentric dimension e4 is thus established between the crank pin 110 and the drive element 102.
  • the crank pin 110 transmits to the connecting rod 111 a stroke which corresponds to twice the smallest overall eccentric dimension e4.
  • the partial eccentricities are not shown to scale in magnitude and direction. Rather, it is preferably provided that the eccentricity e2 can be chosen larger than the eccentricity e1. The result of this is that when the small eccentric dimension e4 is set, the driver 113 on the drive side bears against the stop 115 in every rotational position.
  • crank operation can not only be used for oral irrigators, but can also be used in other fields, for example in general for pump devices or for devices in which a conversion of a rotational movement into a translational movement is to be achieved.
  • the oral irrigator has a plunger pump. This has an improved efficiency compared to known oral irrigation pumps.
  • the plunger pump should have a low-wear drive for the piston.
  • the service life of the piston and the seal should also be increased.
  • the plunger pump 201 in FIG. 19 has a pump housing 202 which has an axially arranged pump inlet 203 and a radially arranged pump outlet 204. At the opposite end of the plunger pump 201, a piston 205 penetrates the pump housing 202. The piston 205 is driven by an eccentric drive 206 or crank drive. The piston 205 has a link guide 207 which receives a link block 208. To move the piston 205, a drive shaft 209 of the eccentric drive 206 or crank drive is set in rotation by an electric motor (not shown).
  • the internal structure of the plunger pump 201 with the pump chamber 210 is shown in FIG. 20.
  • the pump chamber 210 has two connections with the pump inlet 203 and the pump outlet 204, each of which is assigned a check valve 211.
  • the one or more check valves 211 may be spring-loaded.
  • the check valves 211 are aligned such that when the piston 205 moves out of the pump chamber 210, the check valve 11 in the pump inlet 203 opens, while the check valve 211 in the pump outlet 204 is closed.
  • liquid is sucked from a container (not shown) in the oral irrigator via the pump inlet 203 into the pump chamber 210. If the piston 205 moves in the opposite direction, the behavior of the check valves 211 reverses and the liquid is conveyed via the pump outlet 204 to a handpiece of the oral irrigator (not shown).
  • the piston 205 is supported in two bearing points 212, 213, which are located in the pump housing 202.
  • the piston 205 is arranged to be rotatable about its longitudinal axis H.
  • the bearing point 212 on the pump chamber 210 is designed such that the piston end 214 is guided during a stroke between the top and bottom dead center.
  • the bearing point 213 is located at the other end of the pump housing 202.
  • a seal 215 is arranged fixedly in the pump housing 202 in the middle between the two bearing points 212, 213.
  • a sealing lip 216 seals the piston 205.
  • the link guide 207 is arranged on the other end of the piston 205.
  • the link guide 207 has a bore 217 in which the cylindrical link block 208 is arranged.
  • the backdrop or the sliding block 208 is both axially movable and rotatable about the axis V. Due to the rotatable arrangement of the piston 205 and the link or the sliding block 208 about the axes H and V, the piston 205 is practically and gimbally connected to a crank pin 220 of the eccentric drive 206 (or the crank pin 110 of the eccentric drive 101), only with the Difference in that the piston 205 rotates about the axis H instead of being pivoted about an axis which is perpendicular to both axes H and V.
  • the piston 205 and this gimbal or gimbal-like connection allows compensation of a skewed arrangement of the crank pin 220 due to tolerances or elastic and / or plastic or other deformations.
  • a gimbal connection in the sense of this description arises when the piston 205 and the sliding block are rotatable or pivotable about different axes H, V, both axes H and V being perpendicular to one another.
  • the sliding block 208 has a bore 218 lying transverse to the axis V, into which a bearing bush 219 is inserted.
  • the bearing bush 219 is designed to receive the crank pin 220.
  • the crank pin 220 In order to be received in the sliding block 208, the crank pin 220 must penetrate the sliding guide 207.
  • the link guide 207 has an elongated hole 221.
  • the width of the elongated hole 221 is larger than the pin diameter. In this way, contact of the crank pin 220 with the link guide 207 is excluded. The width is chosen so that there is no contact even with a crank pin 220 arranged obliquely.
  • the crank pin 220 moves on a circular path to drive the piston 205.
  • the crank pin 220 and the sliding block 208 are in the top dead center.
  • the piston 205 is located exactly in the middle between its two reversal points, which limit its stroke.
  • the sliding block 208 in the sliding block guide 207 moves down during the first half turn.
  • the piston 205 reaches its rear turning point, which ends the suction process. Up to this point, the check valve 211 in the pump inlet 203 is open, while the other check valve 211 is closed.
  • the piston 205 moves again in the direction of the pump chamber 210.
  • FIG. 21 shows the crank mechanism 206 with the link guide 207 of the piston 205.
  • the crank mechanism 206 has a drive shaft 209 on which a disk 222 is fastened.
  • the disk 222 carries the crank pin 220 arranged with the eccentricity E1.
  • the crank pin 220 extends through the elongated hole 221 of the link guide 207 into the link block 208, where it is received in a bearing bush 219.
  • the plunger pump 201 of a second embodiment in FIG. 22 shows the arrangement of the pump outlet 204 behind the pump inlet 203, both connections being arranged radially on the circumference of the plunger pump 201.
  • the connections 203, 204 are integrated in a pressure piece 223, which is mounted on the plunger pump 201.
  • the piston 205 has a flat 224 on its side facing the pump inlet 203 and the pump outlet 204.
  • the flat 224 ensures a connection of the pump outlet 204 to the pump chamber 210, which is independent of the position of the piston 205.
  • both check valves 211 are each loaded or preloaded with a spring.
  • the piston 205 has three areas with different diameters 225-227, which increase in size from the bearing point 212 to the area of the seal 215 up to the bearing point 213, which is no longer shown. With these stages 225-227 of the piston diameter, a distribution of wear particles occurring in the areas of the seal or the bearing points is avoided.
  • Such a pump can not only be used in any irrigator, but can also be used in other areas, for example in irrigation systems. In principle, it can be used with all pump devices with a piston guide. Other aspects of the cleaning process and irrigator
  • the oral irrigator preferably has two functions (operating modes) or two different spray nozzles that can be used optionally.
  • the speed of the emerging cleaning liquid is low (this speed is preferably below 20 m / s, in particular from 10 m / s to 15 m / s).
  • the flow rate in this oral irrigation function is at least 100 ml / min, in particular 200 ml / min to 400 ml / min, preferably approximately 300 ml / min.
  • the other high pressure function has already been described in detail.
  • the different functions enable the switch eccentric or two different long stroke lengths of the pump.
  • One of the two functions can be set optionally.
  • One function is practically an oral irrigator function, the other a new special function for plaque removal, which is comparable to brushing teeth with a toothbrush or has a comparable cleaning effect. This special function can at least reduce the use of a toothbrush and thus avoid severe abrasion.
  • the special function can also be present in an independent device without an oral irrigation function.
  • a station with two such different oral irrigators is also conceivable, i.e. a low pressure oral irrigator (as one device) and a high pressure oral irrigator as another device, both devices being able to use the same or different pumps.
  • a high-pressure piston pump is preferably provided, which preferably reaches a maximum of approximately 50 to 70 bar, in particular approximately 60 bar.
  • the flow rate is preferably about 50 to 70 ml / min, in particular 60 ml / min.
  • the working distance between the tooth and the nozzle outlet is about 2 - 6 mm.
  • FIG. 25 again illustrates the spray function or the special spray nozzle.
  • Arrow 300 illustrates the eccentrically arranged slots that create the water vortex.
  • the arrow 301 points to the swirl chamber with rotating water.
  • Arrow 302 points to the rotating water, which forms a thin film of water along the conical nozzle outlet.
  • the water film (arrow 303) changes into micro-fine drops at the outlet.
  • the drop size can be changed by the slot geometry and / or the slot distance to the center of the vortex chamber and / or by the angle and / or length of the outlet cone.
  • 26 shows a tooth classification according to "Rustogi".
  • the oral irrigator according to the invention after a cleaning time of only 2 min / dentition, in the aproximal areas (D and F) and in the areas close to the gingiva (A, B and C) over 70% to 80% of the Plaque removed. In the other areas (I, G, H and E) there is even a better cleaning effect. Cleaning is also given in the proximal areas (tooth gaps). This is a very low-abrasion or tooth-friendly cleaning.
  • FIGS. 27 to 29 show the cleaning process using a microfine droplet 310. This impulses impinge on a plaque layer 31 1 via a tooth 312 with high energy (FIG. 27). This energy pushes the plaque outwards (Fig. 28), with a high pressure in the middle of the drop. A crater is created. The pressure shifts outwards, as the two upward arrows in FIG. 29 illustrate.
  • FIGS. 30 to 32 show further embodiments of the spray nozzle which can be combined with the features of one or more of the nozzles described above.
  • Fig. 31 shows a spray nozzle with a full cone steel.
  • 32 shows a spray nozzle with a hollow core.
  • gel jet with which a very gentle cleaning effect can be achieved, the water volume being low.
  • FIGS. 33 and 34 show a spray nozzle with a nozzle attachment, which is preferably designed as a brush ring 320 - preferably with a plastic ring 321 and brush hairs 322 arranged in sectors. This can be fixed or detachably arranged on the nozzle head.
  • the brush ring also has the additional effect of a spacer element, so that there is a fixed (safety) distance between the tooth and the nozzle opening.
  • a function is also conceivable in which the brush ring rotates, in particular alternately in two directions of rotation, similar to an electrical toothbrush, i.e. is moved by an electric drive, in particular a motor drive. Other movements and brush shapes are also possible.
  • a brushless element can also serve as a spacing element.
  • the brush-like nozzle attachment can also be used for a known low-pressure oral irrigator.
  • the invention is not limited only to the examples described. Any combination of the individual features of different examples is possible. In particular, the combination of an oral irrigator according to FIGS. 1 to 7 with an eccentric drive according to FIGS. 8 to 18 and / or with a pump according to FIGS. 19 to 24 is expedient.

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  • Health & Medical Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • General Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Dentistry (AREA)
  • Epidemiology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Animal Behavior & Ethology (AREA)
  • Veterinary Medicine (AREA)
  • Water Supply & Treatment (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oral & Maxillofacial Surgery (AREA)
  • Nozzles (AREA)
  • Cleaning By Liquid Or Steam (AREA)
  • Reciprocating Pumps (AREA)
  • Dental Tools And Instruments Or Auxiliary Dental Instruments (AREA)
  • Brushes (AREA)
  • Catching Or Destruction (AREA)

Abstract

Buse de pulvérisation (1) pour la production d'un jet de liquide pour une douche buccale. Ladite buse comporte un corps (2) possédant une chambre (6) dans laquelle débouche un conduit (5) pour liquide destiné à amener du liquide de nettoyage sous pression. Un orifice de sortie (18, 19) de buse partant de la chambre (6) permet la sortie d'un jet de liquide de nettoyage. La chambre (6) communique avec une chambre de turbulence (15) de section transversale ronde destinée à produire un flux rotatif de liquide de nettoyage, du centre de laquelle part l'orifice de sortie (18, 19) de buse qui se présente sous forme d'une partie étroite pratiquement cylindrique et d'une partie élargie conique adjacente à la partie cylindrique. Le liquide de nettoyage est amené sous haute pression jusqu'à la buse de pulvérisation, et un jet à grande vitesse du liquide de nettoyage sortant est produit par l'orifice de sortie de buse à partir de micro-gouttelettes.
PCT/EP2003/011431 2002-10-17 2003-10-15 Douche buccale et buse de pulverisation pour la production d'un jet de liquide et systeme de nettoyage de dents WO2004034923A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AU2003285294A AU2003285294A1 (en) 2002-10-17 2003-10-15 Mouth rinse and spray nozzle for creating a liquid jet and teeth-cleaning system
AT03778276T ATE464019T1 (de) 2002-10-17 2003-10-15 Munddusche und sprühdüse zur erzeugung eines flüssigkeitsstrahls sowie zahnreinigungssystem
US10/531,484 US8052627B2 (en) 2002-10-17 2003-10-15 Spray nozzle and dental cleaning system
EP03778276A EP1555954B1 (fr) 2002-10-17 2003-10-15 Douche buccale et buse de pulverisation pour la production d'un jet de liquide et systeme de nettoyage de dents
DE50312628T DE50312628D1 (de) 2002-10-17 2003-10-15 Munddusche und sprühdüse zur erzeugung eines flüssigkeitsstrahls sowie zahnreinigungssystem
US13/250,447 US20120021371A1 (en) 2002-10-17 2011-09-30 Spray nozzle and dental cleaning system

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE10248336A DE10248336A1 (de) 2002-10-17 2002-10-17 Verfahren und Sprühdüse zur Erzeugung eines Flüssigkeitsstrahls für eine Munddusche sowie Vorrichtung mit einer elektromotorisch antreibbaren Pumpe
DE10248338A DE10248338A1 (de) 2002-10-17 2002-10-17 Tauchkolbenpumpe
DE10248339A DE10248339A1 (de) 2002-10-17 2002-10-17 Kurbeltrieb
DE10248339.6 2002-10-17
DE10248338.8 2002-10-17
DE10248336.1 2002-10-17

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/250,447 Division US20120021371A1 (en) 2002-10-17 2011-09-30 Spray nozzle and dental cleaning system

Publications (1)

Publication Number Publication Date
WO2004034923A1 true WO2004034923A1 (fr) 2004-04-29

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Country Status (6)

Country Link
US (2) US8052627B2 (fr)
EP (1) EP1555954B1 (fr)
AT (1) ATE464019T1 (fr)
AU (1) AU2003285294A1 (fr)
DE (1) DE50312628D1 (fr)
WO (1) WO2004034923A1 (fr)

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US20090017423A1 (en) * 2004-01-20 2009-01-15 Koninklijke Philips Electronics N.V. Droplet jet system for cleansing
DE102009046405A1 (de) * 2009-11-04 2011-05-05 Continental Teves Ag & Co. Ohg Kolbenpumpe
WO2012074918A3 (fr) * 2010-11-29 2012-11-01 Dentsply International Inc. Dispositif dentaire à émission de laser et procédés associés
CN103153226A (zh) * 2010-09-30 2013-06-12 皇家飞利浦电子股份有限公司 具有替换尖端的用于生成高速水滴的牙齿清洁器具
CN106456300A (zh) * 2014-04-29 2017-02-22 索南多股份有限公司 用于清洁牙齿和牙根管的设备和方法
CN106794055A (zh) * 2014-08-29 2017-05-31 申春雨 利用压缩空气的口腔清洁器
US9675426B2 (en) 2010-10-21 2017-06-13 Sonendo, Inc. Apparatus, methods, and compositions for endodontic treatments
US9788926B2 (en) 2013-12-24 2017-10-17 Braun Gmbh Personal hygiene implement
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US10010388B2 (en) 2006-04-20 2018-07-03 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US10098717B2 (en) 2012-04-13 2018-10-16 Sonendo, Inc. Apparatus and methods for cleaning teeth and gingival pockets
US10363120B2 (en) 2012-12-20 2019-07-30 Sonendo, Inc. Apparatus and methods for cleaning teeth and root canals
US10420630B2 (en) 2009-11-13 2019-09-24 Sonendo, Inc. Liquid jet apparatus and methods for dental treatments
US10722325B2 (en) 2013-05-01 2020-07-28 Sonendo, Inc. Apparatus and methods for treating teeth
US10806544B2 (en) 2016-04-04 2020-10-20 Sonendo, Inc. Systems and methods for removing foreign objects from root canals
US10835355B2 (en) 2006-04-20 2020-11-17 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US11173019B2 (en) 2012-03-22 2021-11-16 Sonendo, Inc. Apparatus and methods for cleaning teeth
US11213375B2 (en) 2012-12-20 2022-01-04 Sonendo, Inc. Apparatus and methods for cleaning teeth and root canals
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US10028811B2 (en) * 2004-01-20 2018-07-24 Koninklijke Philips N.V. Droplet jet system for cleansing
US20090017423A1 (en) * 2004-01-20 2009-01-15 Koninklijke Philips Electronics N.V. Droplet jet system for cleansing
WO2006067760A1 (fr) 2004-12-22 2006-06-29 Koninklijke Philips Electronics, N.V. Systeme assiste par gaz pour la production de gouttelettes liquides dans un systeme de soins buccaux
US10010388B2 (en) 2006-04-20 2018-07-03 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US10039625B2 (en) 2006-04-20 2018-08-07 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US11918432B2 (en) 2006-04-20 2024-03-05 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US10617498B2 (en) 2006-04-20 2020-04-14 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US10835355B2 (en) 2006-04-20 2020-11-17 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US10016263B2 (en) 2006-04-20 2018-07-10 Sonendo, Inc. Apparatus and methods for treating root canals of teeth
US11426239B2 (en) 2006-08-24 2022-08-30 Pipstek, Llc Dental and medical treatments and procedures
US11350993B2 (en) 2006-08-24 2022-06-07 Pipstek, Llc Dental and medical treatments and procedures
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US10420630B2 (en) 2009-11-13 2019-09-24 Sonendo, Inc. Liquid jet apparatus and methods for dental treatments
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US11173019B2 (en) 2012-03-22 2021-11-16 Sonendo, Inc. Apparatus and methods for cleaning teeth
US10098717B2 (en) 2012-04-13 2018-10-16 Sonendo, Inc. Apparatus and methods for cleaning teeth and gingival pockets
US11284978B2 (en) 2012-04-13 2022-03-29 Sonendo, Inc. Apparatus and methods for cleaning teeth and gingival pockets
US10631962B2 (en) 2012-04-13 2020-04-28 Sonendo, Inc. Apparatus and methods for cleaning teeth and gingival pockets
US11103333B2 (en) 2012-12-20 2021-08-31 Sonendo, Inc. Apparatus and methods for cleaning teeth and root canals
US10363120B2 (en) 2012-12-20 2019-07-30 Sonendo, Inc. Apparatus and methods for cleaning teeth and root canals
US11213375B2 (en) 2012-12-20 2022-01-04 Sonendo, Inc. Apparatus and methods for cleaning teeth and root canals
US10722325B2 (en) 2013-05-01 2020-07-28 Sonendo, Inc. Apparatus and methods for treating teeth
US9877801B2 (en) 2013-06-26 2018-01-30 Sonendo, Inc. Apparatus and methods for filling teeth and root canals
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CN106794055A (zh) * 2014-08-29 2017-05-31 申春雨 利用压缩空气的口腔清洁器
US10806544B2 (en) 2016-04-04 2020-10-20 Sonendo, Inc. Systems and methods for removing foreign objects from root canals

Also Published As

Publication number Publication date
US8052627B2 (en) 2011-11-08
US20060097084A1 (en) 2006-05-11
EP1555954A1 (fr) 2005-07-27
EP1555954B1 (fr) 2010-04-14
ATE464019T1 (de) 2010-04-15
AU2003285294A1 (en) 2004-05-04
DE50312628D1 (de) 2010-05-27
US20120021371A1 (en) 2012-01-26

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